CN103452961B - Open central control unit with constant and regulating pump - Google Patents

Open central control unit with constant and regulating pump Download PDF

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Publication number
CN103452961B
CN103452961B CN201310205513.1A CN201310205513A CN103452961B CN 103452961 B CN103452961 B CN 103452961B CN 201310205513 A CN201310205513 A CN 201310205513A CN 103452961 B CN103452961 B CN 103452961B
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CN
China
Prior art keywords
pressure
pump
valve
hydraulic
steering
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Expired - Fee Related
Application number
CN201310205513.1A
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Chinese (zh)
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CN103452961A (en
Inventor
E.哈尼施费格
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of CN103452961A publication Critical patent/CN103452961A/en
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Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/065—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by specially adapted means for varying pressurised fluid supply based on need, e.g. on-demand, variable assist
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/07—Supply of pressurised fluid for steering also supplying other consumers ; control thereof
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/225—Control of steering, e.g. for hydraulic motors driving the vehicle tracks
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2282—Systems using center bypass type changeover valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Abstract

The invention relates to a hydraulic control device used for a movable working machine. The control device is provided with a hydraulic steering device used for adjusting the driving direction, and at least one other hydraulic consuming device. The control device comprises a first pump and second pumps separated from the first pump. The first pump enables hydraulic fluid to be conveyed from a tank to the steering device and the other hydraulic consuming devices. The second pumps enables hydraulic fluid to be conveyed from the tank to the other hydraulic consuming devices. The steering device is provided with a steering valve which is matched with the steering device and can control liquid to flow to the steering device. The steering valve is provided with a steering pressure interface, and steering pressure is applied to the steering pressure interface. Each other hydraulic consuming device is provided with a control valve in an open central construction mode. The control valves can control liquid to flow to the corresponding other hydraulic consuming devices. A priority valve of a three-way pressure balance type is formed. The first pump, the steering valve and at least one control valve are connected through the priority valve.

Description

With open central controller that is constant and adjusting pump
Technical field
The present invention relates to a kind of control device of hydraulic pressure.
Background technology
The control device of such hydraulic pressure is used for mobile working machine particularly with low cost, particularly hydraulic crawler excavator and wheel Formula loader.In the case, one or more parallel connected pumps are set, preferred external gear pump, it has constant extruding Volume, pressurized fluid can be transported to different consumers by it from a tank.As consumer, it is considered to for example move work Make the running driving device of machine, the hydraulic cylinder of digger arm or the transfer for adjusting the travel direction of mobile working machine. In the case, the transfer is for security reasons in a kind of special status.The transfer, particularly its steering Valve, it is necessary to have precedence over other consumers and be supplied to pressurized fluid, so that the mobile working machine is under any circumstance all Can keep turning to.Therefore, a kind of pressure-gradient control valve of three-way pressure scale form is set, via the pressure-gradient control valve by pump and switching valve And at least one control valve couple together.The pressure-gradient control valve is arranged such that preferential to switching valve supply pressurized fluid. Using being controlled with the control valve of open central configuration mode, described to control valve preferably comprehensive for the motion of other consumers Into a control block.Such control block be particularly simply construct and therefore cost economy.
This hydraulic pressure control device the disadvantage is that, when relatively low volume flow demand is only existed, by the constant of pump Transportation flow lose very big energy, while also needing to higher Fluid pressure.This kinestate is for example in the case where there Occur, i.e., only described transfer passive movement.
The content of the invention
The task of the present invention is that the efficiency of the control device of the hydraulic pressure is improved in the way of abnormal cost economy. This proposes a kind of control device of the hydraulic pressure for mobile working machine, and the control device has for adjusting travel direction The consumer of the transfer of hydraulic pressure and at least one other hydraulic pressure, wherein, the control device include the first pump and with The second separate pump of first pump, wherein, first pump can by hydraulic fluid from tank to the transfer and it is described at least The consumer conveying of one other hydraulic pressure, and second pump can by hydraulic fluid from tank to described at least one its The consumer conveying of its hydraulic pressure, wherein, the transfer is equipped with switching valve, and the switching valve can control to go to institute The fluid stream of transfer is stated, wherein, the switching valve has steering pressure interface, is applied with the steering pressure seam Steering pressure, wherein, the consumer of each other hydraulic pressure is equipped with the control valve of open central configuration mode, institute Stating control valve can control the fluid stream of consumer of the other hydraulic pressure for going to arranging, wherein, three-way pressure scale shape is set The pressure-gradient control valve of formula, has been connected first pump with the switching valve and at least one control valve via the pressure-gradient control valve Come, it is characterised in that first pump has the extruding volume that can be adjusted, wherein, discharge pressure actuator, the conveying are set Pressure regulator can so adjust the extruding volume of first pump, i.e. utilized when first pump is conveyed One pump pressure is adjusted on pressure nominal value, wherein, second pump has constant extruding volume, wherein, second pump Only can be conveyed to the consumer of at least one other hydraulic pressure using the second pump pressure, wherein, the conveying Pressure regulator includes reversal valve, and the steering pressure and second pump pressure are connected on the reversal valve, wherein, from institute The pressure nominal value is derived in the outlet pressure for stating reversal valve, wherein, second pump pressure stops via spring-loaded pump Return valve to be connected on the discharge pressure actuator, only when second pump pressure has exceeded default opening pressure differential, The discharge pressure actuator is just opened.
According to the present invention, the purpose is solved in the following way, i.e. the first pump has adjustable extruding volume, wherein, Discharge pressure actuator is set, and it can so adjust the extruding volume of first pump, i.e., described first pressure pump conveying When the first pump pressure for being utilized be adjusted on pressure nominal value, wherein, second pump has constant extruding volume, its In, second pump only can be conveyed using the second pump pressure at least one other consumer, wherein, it is described defeated Pressurization pressure actuator includes reversal valve, and the steering pressure and second pump pressure are connected on the reversal valve, wherein, from The pressure nominal value is derived in the outlet pressure of the reversal valve.Correspondingly, except known with constant extruding volume The second pump outside, also set up one have it is adjustable extruding volume the first pump.Via second pump only to it is described other Consumer supply pressurized fluid.First pump is mainly used in supplying the transfer and right in terms of structure size It is to optimize in the purpose.First pump is correspondingly less and therefore be that cost is economically implemented.But first pump Pressurized fluid can be supplied to other consumers, as long as the transmission capacity of these consumers is not by the transfer Use up.In order to first pump is conveyed with required discharge pressure, the discharge pressure actuator of first pump is via changing It is connected not only to be also connected on the steering pressure on second pump pressure to valve.The outlet of reversal valve and its multiple entrance In such a entrance connection, highest Fluid pressure is applied with the entrance.
The particular advantage of proposed solution is, only with it is less and therefore cost economy the first pump. Such special efficiency for adjusting pump is just obtained by by the proposed mode of connection under such some running statuses, Energy loss is king-sized described in these running statuses.Therefore, improve total system in the way of abnormal cost economy Efficiency.Additionally, for proposed control device only with such as lower member, these components produced in batches and therefore Can cost economically purchased.
The favourable improvement scheme and improving countermeasure of the present invention are given in the following description.
The pressure-gradient control valve can be constructed as follows, i.e., from the first pump fluidly connecting all the time to the switching valve It is to open, wherein, only the pressure of the pump side at the switching valve has exceeded described turn with a default preferential pressure differential During to pressure, just open at least one other fluidly connecting for control valve from first pump, wherein, the pressure is specified Value is poor plus variable rated pressure equal to the outlet pressure of the reversal valve, wherein, the minima of the rated pressure difference is little In the preferential pressure differential.Thus should realize, when other consumers are not operated, first pump is only to institute State transfer to be conveyed.So, first pump only delivery needle needed for the steering, with for needed for turning to The fluid stream of pressure.This so realizes, i.e., the pressure nominal value of described first pump is just so regulated so that described preferential Valve does not decontrol the connection with other consumers.In the case, the minima of the rated pressure difference is preferably different In zero, so that first pump pressure deducts the inevitable pressure drop at the pressure-gradient control valve to obtain the steering pressure Power.When other consumers are not operated, always so adjust.When other consumers and the steering When device is not operated, the extruding volume of first pump is adjusted to zero, wherein, by the minima of rated pressure difference It is adjusted to the first pump pressure.The variable rated pressure difference preferably only has two different values, i.e., aforesaid minima and Maximum described below.
If the transfer passive movement, the steering pressure interface of the switching valve can with the transfer in Press-in connection get up, wherein, if the transfer not passive movement, the steering pressure interface is connected with the tank, Wherein, if the not only steering pressure but also second pump pressure is different from the pressure in the tank, the specified pressure Power difference is elevated above in a value of the preferential pressure differential.Thus achieve, once other consumer quilts Operation, then first pump also can be conveyed to other consumers.This so realizes, that is, improve the pressure Rated value, until the pressure-gradient control valve decontrols the connection with the control valve.In the case, two kinds of situations are distinguished.If described Second pump pressure is more than the steering pressure, then the pressure-gradient control valve is anyway to open, because the pressure nominal value exists Second pump pressure is both greater than in the case of each and therefore more than the steering pressure.If second pump pressure is less than The steering pressure, then the proposed mode of connection is far reaching.Here the pressure nominal value must be actively improved, from And the pressure-gradient control valve decontrols the connection with other consumers.It is only default when having exceeded with the pressure differential of the tank Little threshold value, the threshold value for example can be 5bar, preferably just adopt a kind of pressure different from pressure in the tank.The threshold Value is preferably so selected, i.e., it is more than the idling pressure of second pump.
The discharge pressure actuator can include two pressure valves, and the steering pressure and described is connected at two pressure valve Second pump pressure, wherein, it is poor to improve the rated pressure using the outlet pressure of two pressure valve.In known two pressures In the case of valve, its reversal valve for also referred to as inverting, its outlet is connected with the such a entrance in its multiple entrance, at this Porch is applied with minimum pressure.Can in a straightforward manner cause being proposed above, described by using two such pressure valves The raising of rated pressure difference.
Second pump pressure can be connected on the discharge pressure actuator via spring-loaded pump check-valves, only Have when second pump pressure has exceeded default opening pressure differential, the discharge pressure actuator is just opened.Described second Pump is with the volume flow of constant extruding volume delivered constant all the time, circulation canal stream of the volume flow through the control valve for arranging Move and there cause pressure drop.Therefore, only when other consumers are not operated, second pump pressure is only Different from zero.So, second pump pressure is, for example, 3bar.In order to the idling pressure is it is determined that the pressure nominal value In the case of be not considered, the pump check-valves are set.As long as second pump is only conveyed with the idling pressure, then institute It is to close to state pump check-valves.Therefore second pump pressure is to interrupt with the connection of the discharge pressure actuator.
Multiple other consumers can be set, wherein, each control valve have a circulation canal, when with arrange disappear When fluidly connecting cut-off of device of consumption, the circulation canal is to open, wherein, the circulation canal of all control valves is series connection , wherein, first pump and second pump are connected via the circulation canal of the series connection with the tank.The circulation canal It is to open in the centre position of the opening of known open central configuration mode.Once move consumer, then The connection with the consumer is constantly opened, wherein, while constantly closing the circulation canal.Therefore by described second The constant transportation flow of pump is divided on the circulation canal and the consumer such that it is able to make the consumer with can The speed motion of change.
Circulating pressure scale can be set, lead to the circulation of the circulation canal or the series connection via the circulating pressure scale Road is coupled together with the tank, wherein, the pressure of the control valve side only at the circulating pressure scale is followed more than being subtracted During the second pump pressure of ring compression difference, the circulating pressure scale is just opened.Therefore should realize, when other consumers In one when being operated, second pump pressure is improved immediately.The exact controllability of the control valve is hence improved, its In, the precise control behavior has particularly been started in advance.Particularly no longer need in the consumer motion beginning for arranging Before, just by the control valve with an Invalid path（Totweg）Open.
The circulating pressure difference can be the opening pressure differential of the pump check-valves.When using the circulating pressure scale, It is poor that the idling pressure of second pump is equal to the circulating pressure.Correspondingly, when the idling pressure is it is determined that first pump Pressure nominal value in the case of when should not be considered, it is poor that the opening pressure differential is equal to the circulating pressure.
Pump pressure scale can be set, and via the pump pressure scale, second pump can be transported in the tank, wherein, The pump pressure scale is connected to as follows on the pressure-gradient control valve, i.e., described first pump is at least one control valve conveying when institute The pressure for utilizing can open the pump pressure scale, wherein, the pump pressure scale is in the rest of the cases to close.In the control In the case of device processed, first pump is designed for little volume flow and high pressure, wherein, second pump is for little Pressure and big volume flow designing.Realized by proposed connection, when the maximum delivery pressure of second pump When power no longer be enough to operate other consumers, first pump can carry out defeated to other consumers Send.The triggering pressure of the pump pressure scale determines accordingly by the maximum delivery pressure of second pump.Once described One pump pressure has exceeded the triggering pressure, then second pump is transported in the tank substantially free of pressure, wherein, it is described Other consumers are only also supplied via first pump.It is clear that other consumers are in the running status Only can also be moved with larger power but with less speed although lower.
At least one control valve can be connected respectively via check-valves with first pump and second pump, its side Formula is that the pressurized fluid only can be from the pump for arranging at least one control valve flow.Thus should prevent, first pump With second pump by as motor running.Two pumps are necessary for for this and arrange a separate check-valves respectively.
Description of the drawings
The present invention is below by way of the exemplary detailed explaination of accompanying drawing.Wherein：
Fig. 1 shows the wiring diagram of the first embodiment of the control device of hydraulic pressure of the invention；
Fig. 2 shows the intercepting part of an amplification of in the region of the discharge pressure actuator, Fig. 1；And
Fig. 3 shows the wiring diagram of the second embodiment of the control device of hydraulic pressure of the invention.
Specific embodiment
Fig. 1 shows the wiring diagram of the first embodiment of the control device of hydraulic pressure of the invention.The control dress Putting 10 includes the consumer 30 of a transfer 20 for mobile working machine and multiple other hydraulic pressure.It is described to turn to dress Put the travel direction for adjusting the mobile working machine.The consumer 30 of other hydraulic pressure can be for example described shifting The running driving device of dynamic working machine or the hydraulic cylinder on the cantilever of the mobile working machine.
The transfer 20 is diverted valve 21 and operates, and the switching valve for example can be according to Bosch Rexroth AG（It is rich Generation BOSCH-REXROTH company）Catalogue " Lenkaggregat Typ LAGC（Steering machine set type LAGC）" (job number RD 14365;The version of in October, 2007) construction.The switching valve 21 has two interfaces 26, for connecting（It is unshowned）Steering cylinder, The transfer is moved using the steering cylinder.Also set up pump interface 27, tank interface 28 and steering pressure interface 22.Institute State pump interface 27 to be connected on the pressure-gradient control valve 23, wherein, the tank interface 28 is connected on the tank 11.When the switching valve 21 when not operated, and the steering pressure interface 22 is connected with the tank interface 28.When the switching valve 21 is operated, in institute State at steering pressure interface 22, the pressure at interface 26 is applied with as steering pressure 25, in the seam, pressurized fluid To steering cylinder flowing.
The pressure-gradient control valve 23 can for example according to Bosch Rexroth AG（Bosch Rexroth Corp.）Catalogue " Prioritätsventil Typ LPS（Preferential valve-type LPS）" (job number RD 27548;06 month 2006 version) carry out structure Make.The pressure-gradient control valve 23 is three-way pressure scale, and it couples together an entrance with a first outlet and a second outlet.Described One outlet is connected on the pump interface 27 of the switching valve 21, wherein, the second interface is connected to the consumption of other hydraulic pressure On the control valve 31 of device 30.The valve element of the pressure-gradient control valve 23 is pressed in first position by spring 24, in the first position, The entrance being connected on first pump 40 is connected with the first outlet, wherein, what the second outlet was off. The spring side of the valve element is applied with the steering pressure 25, wherein, it is applied with to go out the first of the valve element in spring offside Pressure at mouthful.The pretightning force of the spring 24 obtains the preferential pressure differential, and it is for example adjusted to 10bar.Once institute The pressure at first outlet is stated with the preferential pressure differential more than the steering pressure 25, then the valve element is all the time to described second The direction motion of position.In the case, the connection with the second outlet is opened all the time, wherein, with the first outlet Connection is slightly throttled.In the case, it is connected in the end position of the second position still still with first outlet Open.
The consumer 30 of other hydraulic pressure is equipped respectively with the control valve 31 of open central configuration mode. In the case of this, it is also possible to which the consumer 30 of multiple other hydraulic pressure is connected on a control valve 31.The control valve 31 A valve block is integrated into into, the valve block is for example according to Bosch Rexroth AG（Bosch Rexroth Corp.）Catalogue " Mitteldruck - Mobilsteuerblock Typ Ml-16 und 32（Intermediate pressure-movement control block type Ml- 16 and 32）" (job number RD 64 263;02 month 1998 version) implementing.The control valve 31 has circulation canal 32, its In, the circulation canal 32 is together in series on all control valves.The second outlet of the pressure-gradient control valve 23 is via check-valves 12a and institute State the circulation canal connection of the first control valve 31 of cascaded structure.Second pump is connected to identical point via check-valves 12b On.The check-valves 12a；12b is so installed so that pressurized fluid only can from arrange the first pump 40 and the second pump 50 to The control valve 31 flows.
As long as during the control valve 31 is centrally located, then with the connection of the consumer 30 of the other hydraulic pressure for arranging It is off, wherein, the circulation canal 32 is full opening of.Once the control valve 31 is operated, then the circulation is logical Road 32 is continuously off, meanwhile, the connection of consumer 30 to the other hydraulic pressure for arranging persistently is opened, and its mode is, The fluid stream of inflow is divided on two flow paths.Therefore the other hydraulic pressure that can infinitely adjust the arranging disappear The movement velocity of consumption device 30.It is described control valve 31 have two direction of operating, so as to can also adjust the arranging other Hydraulic pressure consumer 30 the direction of motion.In the case, from holding that the consumer 30 of other hydraulic pressure flows back Pressure fluid is flowed out in the tank 11 via the separate tank interface 34 of the valve block.
In the end of the cascaded structure of the circulation canal 32, circulating pressure scale 33 is arranged in such a way so that institute Stating circulating pressure scale can be opened by the pressure in the circulation canal 32 to the tank 11.Along closing direction, the circulation Manometric balance is connected on the second pump pressure 51 via pump check-valves 52, and second pump 50 is carried out defeated using second pump pressure Send.The pump check-valves 52 are remained turned-off by spring, wherein, the pump check-valves can be opened by second pump pressure 51. The pretightning force of the opening pressure differential of the pump check-valves 52 corresponding spring in other words is so adjusted, i.e., when second pump is in sky In turning during operation, that is to say, that when the consumer 30 without other hydraulic pressure is operated, the opening pressure differential is in other words The pretightning force is located on second pump pressure 51.In the case, the opening pressure differential of 5bar is for example adjusted out.At this Under state, the circulating pressure scale 33 is not loaded by first pump pressure 51.Once in the consumer 30 of other hydraulic pressure A passive movement, then the pump check-valves 52 are opened, and second pump pressure 51 is being subtracted the opening pressure differential In the case of be applied in the circulating pressure scale 33, the reversal valve 43 and two pressure valve 44.As a result, when control valve 31 When being operated, second pump pressure 51 is raised immediately, until the consumer 30 of the other hydraulic pressure for arranging is moved.
Second pump 50 has constant extruding volume and is preferably configured as external gear pump.Second pump is by pressure-bearing Liquid is only conveyed to the consumer 30 of other hydraulic pressure from tank 11 and not conveyed to the transfer 20.Described Connect pump pressure scale 53 at the pressure interface of the second pump 50, the pump pressure scale is pressed in the position of closing by spring.In bullet Spring offside connects the pressure at the second outlet of the pressure-gradient control valve 23.Once the pressure has exceeded the bullet of the pump pressure scale 53 The pressure of spring is equivalent, then the pump pressure scale is opened and second pump 50 is transported to the tank 11 substantially free of pressure In.As a result, only also have first pump 40 to be conveyed pressurized fluid to the consumer 30 of other hydraulic pressure, but The conveying is carried out with extra high pressure, and the pressure can exceed that the maximum delivery pressure of second pump 50.
Fig. 2 shows the intercepting part of an amplification of in the region of the discharge pressure actuator 42, Fig. 1, its In, for clarity, eliminate second pump 50.First pump 40 suctions out pressurized fluid from the tank 11 and incites somebody to action It is with the first pump pressure 41 to the pressure-gradient control valve（Label 23 in Fig. 1）Conveying.First pump 40 has sustainable regulation Extrude volume and be preferably implemented as Wobble plate pump or inclined shaft pump.The extruding volume is adjusted using cylinder 60 and kicker cylinder 61 is adjusted Section, the regulation cylinder and the kicker cylinder are respectively configured to simple single cylinder.The kicker cylinder 61 is connected to first pump On pressure 41 and cause it is described extruding volume increase.Once as a result, the first pump quilt（It is unshowned）Motor or Internal combustion engine is placed in rotational motion, then first pump is adjusted towards the direction of maximum extruding volume.The kicker cylinder 61 sets There is spring, the spring equally rolls away from the kicker cylinder.Therefore even if first pump 40 is not rotated, also adjust out it is described most Big extruding volume.
It is described adjust cylinder 60 have the opposite effect with the kicker cylinder 61 and therefore cause it is described extruding volume reduction.The tune Section cylinder adjusts manometric balance and second and adjusts manometric balance 62 by first；64 activate.Described first adjusts manometric balance 62 by described first The preferred manually adjustable spring 63 for adjusting manometric balance 62 is pressed in first position, and described in the first position cylinder is adjusted 60 are connected with the tank 11 and with the described second regulation manometric balance 64.In the spring offside, first pump pressure 41 is applied It is added in described first to adjust on manometric balance 62 such that it is able to the described first regulation manometric balance 62 is moved in the second position, In the second position, the regulation cylinder 60 is connected with first pump pressure 41.Therefore, when first pump pressure 41 exceedes The pressure equivalent time adjusted on the spring 63, first pump is adjusted towards the direction of little extruding volume.Therefore, it is described First regulation manometric balance 62 causes the restriction upwards of first discharge pressure 41.
The second regulation manometric balance 64 is pressed in first position by the spring 65 of the described second regulation manometric balance 64, Adjust cylinder 60 described in the first position to be connected with the tank 11 via the described first regulation manometric balance 62.Adjust described second There is first pump pressure 41 in the spring offside of manometric balance 64 such that it is able to which the described second regulation manometric balance is moved to into second In position, cylinder 60 is adjusted described in the second position and is connected with first pump pressure 41 via the described first regulation manometric balance 62 Connect.The spring 65 is designed with spring regulating device 66, the spring regulating device can by the pretightning force of the spring 65 with The preset value of such as 4bar is improved.The spring regulating device 66 is operated via two pressure valve 44, wherein, when described two When the pressure in the exit of pressure valve 44 has exceeded the pressure in the tank 11 with default little threshold value, there is carrying for the pretightning force It is high.
Additionally, the spring side of the second regulation manometric balance 64 is connected to the exit of the reversal valve 43.Additionally, described The spring 65 of the second regulation manometric balance 64 is preferably able to regulation manually, wherein, the pressure for for example adjusting out 8bar is equivalent.Therefore, The pressure nominal value adjusted out on the described second regulation manometric balance 64 is that the pressure in the exit of the reversal valve 43 is added Rated pressure is poor.The minima of the rated pressure difference is that the pressure adjusted out on the spring 65 is equivalent, such as 8bar.Institute Stating rated pressure difference can bring up to 12bar by the spring regulating device 66 from such as 4bar.Therefore, the rated pressure Difference less than the preferential pressure differential and is higher than quickly again quickly the preferential pressure differential, and the preferential pressure differential is, for example, 10bar.This is depended on, during whether the relatively low pressure applied at the two entrances of two pressure valve 44 is higher than the tank 11 Pressure.The steering pressure 25 is applied with two pressure valve 44 and the of the opening pressure differential of pump check-valves 52 has been subtracted Two pump pressures.Therefore, only when the transfer（Label 20 in Fig. 1）And in the consumer of other hydraulic pressure At least one（Label 30 in Fig. 1）All passive movement when, just there is the raising of rated pressure difference.In the reversal valve 43 Porch be equally applied with described two pressure, wherein, be applied with described two pressure in the exit of the reversal valve 43 In higher pressure and be applied to it is described second adjust manometric balance 64 spring side.
Fig. 3 shows the wiring diagram of the second embodiment of the control device 10 of hydraulic pressure of the invention.Described second Embodiment is to construct identically with first embodiment in addition to the difference being described below, therefore is come with regard to this respect Say the embodiment for being referred to Fig. 1 and 2.In the case, identical part is represented with identical reference.
In the case of second embodiment, for clarity, the circulating pressure scale and the pump pressure are eliminated Scale.But described part can also easily be supplemented in and, to obtain the advantage with reference to described by first embodiment.
First embodiment and second embodiment differ primarily in that the pressure nominal value for determining first pump 40 Ways and means.In the case, the spring regulating device is eliminated on the described second regulation manometric balance 64（In Fig. 2 Label 66）, provide so as to the component being made up of first pump 40 and discharge pressure actuator 42 and commercially in batches Structural regime is consistent.The pressure nominal value is only added by being applied to the pressure of the spring side of the second regulation manometric balance 64 The pressure equivalence of such as 8bar adjusted on the spring draws.So-called pressure equivalence is also that the rated pressure is poor Minima.
Described second regulation manometric balance 64 spring side pressure be reversal valve 43 exit pressure, the reversal valve Including three separate check-valves.Therefore the reversal valve includes three entrances, wherein, it is applied with described three in exit and enters Highest pressure at mouthful.One in the entrance is connected with the steering pressure 25.Another entrance and second pump Pressure 51 connects.3rd entrance is connected with rated pressure scale 68.The rated pressure scale 68 is pressed into the position of closing by spring In, wherein, spring side is also applied with the steering pressure 25.The spring is for example tightened in advance on the pressure of 4bar equivalence. Spring offside is applied with the pressure between the rated pressure scale 68 and the reversal valve 43.Therefore, the rated pressure scale 68 can be adjusted to the pressure in one value, and the value is beyond the bullet that the size of the steering pressure 25 is the rated pressure scale The pressure of spring is equivalent, such as 4bar.But with the proviso that, the two position two-way valve 67 is linked in open position, wherein, The rated value manometric balance 68 is connected via the two position two-way valve with first pump pressure 41.But the two position two-way valve 67 It is pressed in the state of closing by spring.Connect the outlet of two pressure valve 44 in the spring offside, in described two pressures The porch of valve connects the steering pressure 25 and second pump pressure 51.When the transfer 20 and the control valve 31 One of when all being operated, the two position two-way valve 67 is linked in open position.
It should be noted that the check-valves 52 of the reversal valve 43 are provided with return spring, wherein the check-valves be arrange to Second pump pressure 51, only when second pump pressure 51 has exceeded idling pressure, the check-valves are just opened.Institute State return spring to be for example tightened in advance on the pressure of 5bar equivalence.Therefore, the check-valves 52 also have the according to Fig. 1 and 2 The function of the pump check-valves of one embodiment.
Reference numerals list
The control device of 10 hydraulic pressure
11 tanks
12a check-valves
12b check-valves
20 transfers
21 switching valves
22 steering pressure interfaces
23 pressure-gradient control valves
The spring of 24 pressure-gradient control valves
25 steering pressures
26 interfaces
27 pump interfaces
28 tank interfaces
The consumer of 30 other hydraulic pressure
31 control valves
32 circulation canals
33 circulating pressure scales
The tank interface of 34 valve blocks
40 first pumps
41 first pump pressures
42 discharge pressure actuators
44 2 pressure valves
50 second pumps
51 second pump pressures
52 pump check-valves
53 pump pressure scales
60 adjust cylinder
61 kicker cylinders
62 first adjust manometric balance
63 first springs for adjusting manometric balance
64 second adjust manometric balance
65 second springs for adjusting manometric balance
66 spring regulating devices
67 two position two-way valves
68 rated value manometric balances.

Claims (9)

1. the control device of the hydraulic pressure of mobile working machine is used for（10）, the control device has for adjusting the liquid of travel direction The transfer of pressure（20）With the consumer of at least one other hydraulic pressure（30）,
Wherein, the control device includes the first pump（40）And the second pump separated with the first pump（50）, wherein, first pump （40）Can be by hydraulic fluid from tank（11）To the transfer（20）Consumption with least one other hydraulic pressure is filled Put（30）Conveying, and second pump（50）Can be by hydraulic fluid from tank（11）To at least one other hydraulic pressure Consumer（30）Conveying,
Wherein, the transfer（20）It is equipped with switching valve（21）, the switching valve can control to go to the transfer （20）Fluid stream, wherein, the switching valve（21）With steering pressure interface（22）, apply in the steering pressure seam There is steering pressure（25）,
Wherein, the consumer of each other hydraulic pressure（30）All it is equipped with the control valve of open central configuration mode （31）, the consumer for controlling other hydraulic pressure that valve can control to go to arranging（30）Fluid stream,
Wherein, the pressure-gradient control valve of three-way pressure scale form is set（23）, via the pressure-gradient control valve by first pump（40）With it is described Switching valve（21）And at least one control valve（31）Couple together,
Characterized in that, first pump（40）With the extruding volume that can be adjusted, wherein, discharge pressure actuator is set （42）, the discharge pressure actuator can so adjust first pump（40）Extruding volume, i.e. by first pump （40）The first pump pressure utilized during conveying（41）It is adjusted on pressure nominal value,
Wherein, second pump（50）With constant extruding volume, wherein, second pump utilizes the second pump pressure（51）Only Can be to the consumer of at least one other hydraulic pressure（30）Conveyed,
Wherein, the discharge pressure actuator（42）Including reversal valve（43）, the steering pressure is connected on the reversal valve （25）With second pump pressure（51）, wherein, from the reversal valve（43）Outlet pressure in derive the pressure nominal value,
Wherein, second pump pressure（51）Via spring-loaded pump check-valves（52）It is connected to the discharge pressure actuator （42）On, only when second pump pressure（51）When having exceeded default opening pressure differential, the discharge pressure actuator is Open.
2. according to the control device of the hydraulic pressure described in claim 1, it is characterised in that the pressure-gradient control valve（23）Structure as follows Make, i.e., from first pump（40）To the switching valve（21）Fluidly connect what is be always on, wherein, only when described turn To valve（21）The pressure of the pump side at place has exceeded the steering pressure with a default preferential pressure differential（25）When, from described first Pump（40）To at least one other control valve（31）Fluidly connect just open, wherein, the pressure nominal value be equal to it is described Reversal valve（43）Outlet pressure it is poor plus variable rated pressure, wherein, the minima of the rated pressure difference is less than described Preferential pressure differential.
3. according to the control device of the hydraulic pressure described in claim 2, it is characterised in that when the transfer passive movement, institute State switching valve（21）Steering pressure interface（22）With the transfer（20）In pressure be connection, wherein, when described Transfer（20）Not during passive movement, the steering pressure interface（22）With the tank（11）It is connection, wherein, when described turn To pressure（25）With second pump pressure（51）All with the tank（11）In pressure it is different when, the rated pressure difference is carried In a high value to higher than the preferential pressure differential.
4. according to the control device of the hydraulic pressure described in claim 3, it is characterised in that the discharge pressure actuator（42）Including Two pressure valves（44）, the steering pressure is connected at two pressure valve（25）With second pump pressure（51）, wherein, using institute State two pressure valves（44）Outlet pressure, it is poor to improve the rated pressure.
5. according to the control device of the hydraulic pressure described in claim 1, it is characterised in that arrange the consumption dress of multiple other hydraulic pressure Put（30）, wherein, each control valve（31）With a circulation canal（32）, when the consumer with the other hydraulic pressure for arranging （30）When fluidly connecting cut-off, the circulation canal be open, wherein, all control valves（31）Circulation canal（32）It is Series connection, wherein, first pump（40）With second pump（50）Via the circulation canal of the series connection（32）With the tank （11）Connection.
6. according to the control device of the hydraulic pressure described in claim 5, it is characterised in that arrange circulating pressure scale（33）, via institute Circulating pressure scale is stated by the circulation canal（32）The circulation canal of the series connection in other words（32）With the tank（11）Connect Come, wherein, only when the circulating pressure scale（33）The pressure of the control valve side at place is more than being subtracted the of circulating pressure difference Two pump pressures（51）When, just open the circulating pressure scale（33）.
7. according to the control device of the hydraulic pressure described in claim 6, it is characterised in that the circulating pressure difference is the pump non-return Valve（52）Opening pressure differential.
8. according to the control device of the hydraulic pressure described in claim 1, it is characterised in that arrange pump pressure scale（53）, via described Pump pressure scale, second pump（50）The tank can be transported to（11）In, wherein, the pump pressure scale（53）As follows It is connected to the pressure-gradient control valve（23）On, i.e., described first pump（40）To at least one control valve（31）The pressure utilized during conveying The pump pressure scale can be opened（53）, wherein, the pump pressure scale is in the rest of the cases to close.
9. according to the control device of the hydraulic pressure described in claim 1, it is characterised in that at least one control valve（31）Respectively Via check-valves（12a;12b）With first pump（40）With second pump（50）Connection, its mode is that pressurized fluid is only capable of Enough the first pumps from arranging（40）With the second pump（50）To at least one control valve（31）Flowing.
CN201310205513.1A 2012-05-29 2013-05-29 Open central control unit with constant and regulating pump Expired - Fee Related CN103452961B (en)

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DE201210208938 DE102012208938A1 (en) 2012-05-29 2012-05-29 Hydraulic control device for mobile working machine e.g. hydraulic excavators, has delivery pressure regulator that includes shuttle valve connected to steering pressure and pump pressure, such that pressure set-point is derived

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